Hydraulic transmission control



Feb. 18, 1947. A. L. JOHNSON ETAL 2,415,885

HYDRAULIC TRANSMISSION CONTROL Filed May 13, 1943 9 Sheets-Sheet l m ATTORNEY a Feb. 18, 1947.

A. L. JOHNSON ET AL HYDRAULIC TRANSMISSION CONTROL 9 Sheets-Sheet 2 Filed llay 13, 1943 QWN } 0M .mafl w m. ATTORNEY a Feb. 18, 1947. A. JOHNSON ETAL HYDRAULIC TRANSMISSION CONTROL 9 sheets-sheet 5 Filed May 13, 1943 mm 9% a 8% m8 kw w an Q Q Q 2 mm mm ww aw N mx bx fin "saw man ,8

Feb. 18, 1947. A. L. JOHNSON ETAL 21415385 HYDRAULIC TRANSMI SS ION CONTROL Filed May 13, 1943 9 Sheets-Sheet 4 INVENTOR AMI Joflmon/ BY SeflnwuA. I6

ATTORN EY Feb. 18, 19,47. A. 1.. JOHNSON EIAL 2,415,885

' HYDRAULIC TRANSMISSION CONTROL I v Filed May 1:5, 194: 9 Sheets-Sheet 5 I ll A A- INVENTOR ATTORNEY Feb. 18, 1947. A. JOHNSON ETAL 2,415,

HYDRAULIC TRANSMISSION CONTROL Filed m 15, 1945 9 Sheets-Sheet 6 REVERSE SIXTH Feb. 18, 1947. v A. L. JOHNSON ETAL 2,415,885

HYDRAULIC TRANSMISSIOR CONTROL Filed May 13, 1943 9' Sheets-Sheet 7 NEUTRAL? F! RsT SECO ND TH|RD* FOURTH 311 FIFTH SIXTH' SEVENTH C2 Bl 02 El F2 Al 4 03- 82' Cl E2 DI NEUTRAL FIRST 42? szco-0- THIRD ou RTH- FIFTH SEVENTH EIGHT NINTH TENTH 456 460 468 4 29 mvzmon 7 lav-EMA. m 29100:?

ATroR'NEY 1 7. A. L. JOHNSON ET L 2,415,885

mmmuuc TRANSMISSION con'moz.

Filed May 13, 1943 9 Sheets-Sheet 8 an an an 8s mam.

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ATTORNEY a Feb. 18, 1947. I A. JOHNSON :rm. 3 3

HYDRAULIC TRANSMISSION CONTROL Filed May 13, 194:5 9 Sheets-Sheet 9 INVENTOR Q Q (06L6-Z.J0/Zndon BY 5 UwzAhK/ 't' Q ATTORNEY atented m. 18,394?

2,415.8 HYDRAULIC TRANSMISSION CONTROL Albert L. Johnson and Selmer A. Kraft, St. Paul,

Minn., assignors to Johnson Poweron Transmission Corporation, St. Paul, Minn., a corporation of Minnesota Application May 13, 1943, Serial No.'486,809

7 Claims.

1 ,Our invention relates .to an improvement in hydraulic transmission control, wherein it is desired to provide 'an apparatus capable of controlling the operation of atransmission or the I like.

' In a co-pending application filed in the name of Albert L. Johnson, Serial No. 384,792, a planetary type transmission was described embodying friction type clutches to hold various elements of the transmission from relative rotation. While this previously described transmission was entirely successful in its operation, certain advan-' tages were felt to exist in a hydraulic clutch arrangement capable of taking the place of the friction clutches.

It is the object of the present invention to provide a hydraulic control for a transmission or the like capable of holding various elements of the transmission from relative rotation. In some instances it is desired to hold two rotatable elements together to cause rotation of these elements in unison. In other instances it is desired to hold certain rotative parts stationary. Our hydraulic clutch mechanism is capable of accomplishing these results in a simple and'efiective manner.

A feature of the present invention lies in the provision of a clutch embodying a fixed casing, a rotative member rotatably supported in said casing, and a second relatively rotatable element independently rotatable within the first named rotatable element. Means are provided for look-- ing the two relatively rotatable members together for operation in unison and means are also provided for locking one of the rotatable members vin stationary position. This double action of the clutch device renders the same capable of accomplishing atmultiplicity of difierent results. I

A feature of the present invention lies in the provision of a clutch device comprising a rotatable element within a casing and in providing vane means in the rotatable element engageable with the casing. The rotatable element is held stationary when so desired by projection of the vanes into engagement with a cam-shaped pocket in the casing. When preferred, however, the vanes may be retracted "into the rotatable member to rotate therewith without. creating undue friction or back pressure, and without the necessity of circulating oil.

A further feature of the present invention lies in the provision of an inner rotatable member positioned within an outer rotatable element and in the provision of a cam-shaped outer surface on the inner rotatable member which is engageable with the vane means on the outer rotatable member. As a result when the vane means project inwardly from the outer rotatable member they may act to prevent relative rotation between the two relatively rotatable elements. However, when the vane means are in outwardly projecting position the same vane means may act to hold the outer rotatable member stationary in its casing.

A further feature of the present invention lies in the provision of locking means capable of hold- .ing the vane means in intermediate position retracted into the outer rotatable element. Thus the two rotatable members may rotate relative to each other and relative to the casing without undue friction or circulation of hydraulic liquid.

A further feature of the present invention lies in the provision of an automatic control capable of actuating the vane means carried by the outer rotatable member. This control is operable in response to the volume of liquid pumped by a suitable liquid'pump connected to the drive shaft of the power unit driving the transmission. Thus as the speed of the driving unit increases the volume of liquid pumped will increase, operating through the control to change the gear ratio between the driving and the driven shaft.

A feature of the present invention lies in the fact that our control operates in response to torque exerted upon the driven element. If the torque load on. the driven element suddenly increases there is an instant tendency for the driven element to decrease in speed, which in turn reduces the volume of liquid pumped to the control. The speed ratio may be changed under various conditions. First, the ratio may change by varying the speed of the driving motor. I Second, upon acceleration of the motor the speed ratio may at pressure on opposite sides of each vane is equalvary. Third, the idling adjustment, or da'sh adjustment has a bearing on the speed ratio and the time required .to change from one speed ratio to the next. In the fourth, place, the control may be set to limit change of speed ratio. In the fifth place, manual operation of the control may take place when desired. Finally, when'so desired, the.

automatic control may function to vary the speed ratio through an entire range of speeds from a low speed to a high speed ratio with a single op-' eration of the manual control.

An additional feature of the present invention lie in theprovision of a clutch in the iorm'of a vane pump, in which a rotor supporting slidable vanes is mounted for cooperation with a camshaped surface. "Means ,are provided whereby Figure 14.

ized during the sliding movement of the vane, or during projection or retraction of each vane.

These and other objects and novel features of our invention will be more clearly and fully set forth in the following specification and claims.

In the drawings forming a part of our specification:

Figure 1 is a side elevational view, partly in section, showing our transmission and controlling unit therefor. 1

Figure 2 is a transverse section taken substantially on the line 2-2 of Figures 1 and 3.

Figure 3 is a longitudinal section through onehalf of the transmission on substantially the line 3-3 of Figures 1 and 2.-

Figure 4 is a vertical section taken substantially on the line 4-4 of Figure 1.

Figure 5 is a sectional view taken on substantially the line 55 of Figure 4.

Figure 6 is'a section taken substantially on the line 6-6 of Figure 4.

Figure 7 is a sectional view taken substantially on the line 1-1 of Figure 4.

Figure 8 is a sectional view taken on the line 8-8 of Figure 4.

Figure 9 is a sectional view, the position of the section being shown by the line 99 of Figure 4.

Figure 10 is a diagrammatic view showing a valve cylinder in diagrammatic form.

Figure 11 is a sectional view through the transmission, the position of the section being indicated by the line lI-ll of Figure 3.

Figure 12 is a sectional view. through a clutch unit, the position of the section being indicated by the line |2l2 of Figure 3.

Figure 13 is a diagrammatic view of the control valve.

Figure 14 is a sectional view partiallythrough a modified form of transmission control.

Figure 15 is a cross-sectionalview through the vane locking plunger mechanism.

.Figure 16 is across-sectional view through a clutch unit of the transmission illustrated in 'Figure 17 is a diagrammatic view of the control valve used withthe construction of Figure 14.

The transmission is best illustrated in Figures 1 and 3 of the drawings, Figure 1 illustrating the outer appearance thereof, while Figure 3 is a is attached. Thus, upon rotation of the engine crank shaft, the gear housing I4 is rotated through the hub l3. The driven shaft 15 is preferably coaxial with the drive shaft connected to the hub l3 and coaxial with the gear housing l4. Sleeves l6, l1, and I9 encircle the driven shaft l5, extending'various lengths longitudinally of the same, as will be later more fully described in detail. The sleeve is freely encircles the shaft l5 and may rotate with respect thereto. The sleeve ll encloses a portion of the sleeve I6, while the sleeve l9 encloses a portion of the sleeve H.

The gear housing I4 is formed of two portions, one of which includes a disk member 20 extending radially outwardly from the hub l3 and having a hollow cylindrical flange 2| projecting laterally therefrom near the outer extremity thereof. A

' rin var 22 is secured to the outer peri her of transverse section through slightly more than do one-half of the same. The transmission gears are enclosed 'by an inner gear housing positioned within a tapered housing or enclosure l0 having an attachment flange ll thereon, by means of which the housing maybe secured to the drive unit which may comprise an internal combustion engine or the like. As viewed from the top, as in Figure 3, the cone-shaped portion III of the casing bulges outwardly to some extent because of the operating valves which are positioned on opposed sides of the transmission housing. The

flange II is secured to the power unit by anysuitable means such as cap screws 12.

The following description involves an epicyclic gear transmission system, a clutch system for controlling the rotation of various elements thereof, and a control system for hydraulically controlling the clutch system. For the purpose of clarity, these systems will be described in succession.

the engine drive shaft, not illustrated in the drawings is preferably equipped with an end the disk 20 so that the housing l4 may be rotated by a starting motor, when desired, for starting the engine. A second portion of the housing 14 includes a hub 23 supported by a bearing on the end wall'of the housing I0 which will be later described,- and supports .a bearing 24 encircling the sleeve IS. A disk 25 extends outwardly from this hub 23.for supporting a cylindrical-shell 26 of smaller diameter than the cylindrical flange 2|. A ring-shaped flange 21 is provided on the extremity'of the cylindrical shell 26 and this flange 21 is secured to the cylindrical flange 2i by cap screws 29 or other suitable means. Thus a gear housing is provided, one end of which is secured to the drive shaft for rotation therewith, and the other end of w'hichis supported by the stationary housing Ill. The disks 20 and 25 form the ends of the housing l4, while the connected cylindrical shells 2| and26 form a gear enclosure. A sun gear 30 is provided on the driven shaft l5, being splined thereto at 3| and being concentric with the drive shaft. The sun gear 30 is continuously meshed with the gear teeth 32 of the double pinion 33. In actual construction a plurality of such double pinions are supported in angularly spaced relation about the sun gear 30, as better illustrated in the above mentioned copending application. For the purpose of illustration; however, it is necessary to show but one of these double pinions in order to understand the operation of the present device. The double pinion 33 forms the planet gear means of one epicyclic gear system. The double pinion 33 is supported by a bearing 34 encircling a stub shaft 35. The stub shaft 35 is supported at one end by a disk-shaped support 36, which in turn is supported by a bearing 31 encircling a portion of the hub l3 of the gear casing H. A bearing 39 is provided between the disk-shaped support 36 and the sun gear 30 mounted on the driven shaft 15. Thus the support 36 is freely rotatable both with respect to the drive shaft and with respect to the driven shaft. The disk-shaped support 36 is peripherally keyed to a rotor 40 forming the rotative element of a clutch R. The construction of this clutch will be more fully described.

The teeth 4| of the double pinion 33 are meshed with a sun gear 42 rotatable with the sleeve "5. The sleeve I6 is supported rotatably upon .the shaft l5 and a bearing 43 therebetween prevents excessive friction and wear between the shaft l5 and the sleeve 16 and between the sun gears 30 and 42, caused by end thrust of the sleeve l6 due a to helical construction of the sun gears. The teeth M of the double pinion 33 also engage an internal ring gear 44 upon a rotatable sleeve 45. The sleeve 45 is supported by a central disk 46 mounted upon a bearing 41 engaging a cylindrical flange 59 on a disk 50. The disk 56 extends parallel to the disk 36 and in spaced relation thereto, and forms a bearing for one end of the stub shaft 35. However, intermediate angularly spaced double pinions 33, and in angular relation thereto, the disks 36 and 50 are bolted together to rotate in unison and to act as a single unitary supp r From the foregoing description it will be'noted' that we have provided a planetary or epicyclic gear system including sun gears 30 and". a double pinion 33 engaging both of these sun gears, and a ring gear 34 engaging the teeth ll of the double pinion 33. The sun gears 36 and 42 are of different diameter, the sun gear 30 bein of greater diameter than the sun gear 42, and

' the pinion formed by the teeth 32 being of smaller diameter than the pinion formed by teeth M- The disks 36 and 50 supporting the stub shaft 35 form a planetary gear carrier for the planet gears 33 connectingthe sun gears 36 and 32 to the ring gear 46. The ring gear, the sun gears 30 and 82, and the planetary gears 33 are'a'll sup ported for relative rotation and likewise the planet gear carrier comprising disks 36 and 60 may revolve independently of these gears.

The disk 50 assists in supporting the sleeve i6 by means of a bearing 5! so that the planet gear carrier and the sleeve may rotate freely about their respective axes. Thedisk 46, supporting the sleeve 65 bearing the ring gear 44, could likewise be supported by some other element, but for the sake of convenience the bearing 39 is provided separating this disk 48 from-a cylindri cal flange B9 on the disk 56. A second epicyclic gear system is likewise provided within the gear casing id. This second gear system is connected to the first system through the ring gears of the respective systems, the sleeve 65 being provided with a second internal ring gear 52 at the extremity thereof opposite the internal ring gear at The two ring gears M and 52 are of different diameters, the gear 52 being shown larger in diameterthan the gear 4d.

A sun gear 53 is mounted upon the end of the sleeve H and is rotatably supported bye, bearing 63 interposed between the sleeve I? and the hub of the planet gear carrier disk 55'. This planet gear carrier disk. -55 in turn supports a bearing 56- between the disk 55 andthe hub of the gear carrier disk 60. Thebearing 5d absorbsend thrust of sleeve i1 due to helical formation of the teeth of the sun gear 53.

p A second sun gear 57 is mounted upon the sleeve IS. A thrust bearing 59 is interposed be-' tween the end of the sleeve l9 and thesun gear 53 to hold these elements in proper relation and to absorb end thrust-c due to helical formation of the 'angularly spaced shafts 60 so, as to rotate as a unit. The sole purpose of the disk 55 'isto form a second support for the stub shaft 60. or for the 70 described as follows.

to be transmitted to the driven shaft i5 while" 5 pinion teeth 63 designed to engage the sun gear 53 and the pinion teeth 65 designed to engage the sun gear 51 on the sleeve 19. The teeth 63 and 64 form pinions of different diameters so as to provide additional speed ratios between the drive shaft and the driven shaft.

I The teeth 64 of the double pinion 6| also engage the internal ring gear 52 so as to complete a second epicyclic gearsystem. The planet gear means or double pinion 6| is carried by the stub shaft 66 which revolves about the driven shaft l5 at the same speed as the drive shaft, as the gear carrier comprising disks 25 and 55 form part of the housing M which is directly connected to the drive shaft. The sleeves l1 and I3, as well as the ring gear sleeve 45, are all relatively rotatable. By holding various of these sleeves stationary and by holding various combinations of the sleeves from relative movement, varying speeds will be transmitted from the drive shaft to the driven shaft i5. The clutch R will be described in connection with the transmission,as it isembodied directly within the transmission housing I4. This clutch R may be constructed as. best indicated in Figure 11 of. the drawings. The internal surface of the flange 2| of the gear casing I4 is provided with oppositely disposed arcuate surfaces, and with a pair of oppositely disposed pockets 65. These pockets 65 have a base portion 66 which is concentric with the casing It. The ends 63 of the pockets 65 are inclined or cam-shaped to guide j the cooperating vanes inwardly or outwardly in the manner which will be hereinafter .described.

The rotor is provided with a series of slots 61 40 therein which support radially proi ble vanes 69. The vanes 69 are urged outwardly into the pockets 65 by means of-springs 10 mounted at thebase of the wines. A passage H is connected through the housing disk 26 from each end of each pocket 65 to a ring-shaped valve chamber The valve chamber I2,

V 1| by means of a spring i l. By application of pressure through a'pressure port 15, the valve 13 may be moved slidably to the left as viewed in Figure 3 of thedrawings, opening the passages H and inter-connecting these various passages.

When the passages H are inter-connected the rotor 30 may rotate with respect to the housing M l l thereby permitting relative movement bev tween the planet gear carrier 36, 56 with respect to the casing I4, and accordingly with respect to the drive shaft. When the valve 13 is closed, however, the rotor '46 and accordingly the gear carrier 36, 50 is locked with respect to the. casing l4.

Upon the application of sufficient pressure, which is transmitted past the valve 13 through the passages H to the pockets 65, the vanes 69 55 will be held inwardly by pressure, thus permitting free. rotation of the rotor 40 with respect to the casing or housing ll with the radially slidable vanes 69 retracted.

The operation of the transmission may be When. a reverse speed is the drive shaft rotates in a. forwar direction, the valve'13 is clos d so that the rotor 40 is locked with respect 0 the drive shaft," Simultaneously, a locking means, which will be later r described, is set into. operation, which will halt rotation of the sleeve l1, therebystopping rotation of the sun gear 53. With the sun gear 53' g held stationary, rotation of the drive shaft causes rotation of both of the gear carriers 35, 50 and 25, 55 in unison as the gear carrier 35, 50 is locked to the rotor 41!. Power is then transring ,gear 52 which operates in unison with the ring gear 44. Thus' the rotation of the ring gear 44 is controlled by holding the sun gear 53 stationary, and as the gear carriers supporting the double pinions 33 and rotate in unison with the drive shaft, a reverse rotation is transmitted from the gear 32 to the sun gear 30 on the driven shaft l5.

In further explanation, as the sun gear 53 is held fixed and as the gear carriers rotate at the same speed, the double pinion unit 6| revolves about the sun gear 53, which causes the ring gears 52 and 44 to rotate in set relation thereto. The sun gear 30 on the driven shaft i5 is revolved in a reverse direction faster than it is carried forward by the transmission, acting to rotate the driven shaft l5 in a reverse direction at a ratio of 5.24 to 1 with respect to the drive shaft in the transmission illustrated.

In order to place the transmission in neutra mitted through the double pim'on unit 5! to the position the valve 13 remains closed but the sleeve H is released, permitting the sun gear'53 to rotate. Because of the closure of the valve 13 the clutch R remains locked rotating the rotor mitted to the driven shaft 15, and therefore the transmission is in neutral.

When it is desired tomove the driven shaft l5 forwardly at a low rate of speed, the clutch R remains engaged to lock the rotor 40 to the casing 14, and in addition the sleeve I9 is held from rotation, thereby holding the sun gear 5! stationary. The double pinion 6| is then caused to rotate about the sun gear 51. -By means of the double ring gear 52, 44 movement is transmitted to the double pinion unit 33 which causes rotation of the sun gear on the'driven shaft IS.

The relative rotation of the 'gear units 51 and 33 provides a forward rotation of the driven shaft of 5.77 to lwith respect to the driving shaft in the particular transmission illustrated.

When an increased speed of the driven shaft Iii-i required, the sleeve I9-is released, and the sleeve I6 is held from rotation. The clutch R remains locked so that both planet gear carriers rotatein unison. This action stops rotation of the sun gear 42, causing the double pinion unit 33 to rotate about the sun gear 42, and causing the gear 32 of this unit to rotate the sun gear 30 on the driven shaft l5 at a speed ratio of 3.95 to 1 in the transmission illustrated with respect to the drive shaft. a

When the next higher speed of the'driven shaft is desired, the clutch R is released, while the sun gear 42 remains stationary. At thesame time means are providedto lock the sun. gear 53 from rotation. This locking of the sun gears 42 and 53 from rotation results in a rotation of the ring gear 44, 52 and of the double gear unit 33 which around the larger sun gear 53 and thereby trans- .mitting increased speed of rotation to the ring held stationary. In this po ition the sun gears 42 and 53 are not held stationary, but are merely clutched against relative rotation while the sun "gear 51 is locked in stationary position. The

gear unit 6| is forced to revolve about the sun gear 51 and to provide a definite rate of rotation of the ring gear unit 44, 52 and of the sun gears 42 and53. This action produces a rate of rotation of the driven gear 30 on the driven shaft I5 which is 1.71 to 1 with respect to the drive shaft in the particular transmission illustrated.

In the next higher speed of the driven shaft I5, this driven shaft I5 is rotated atthe same speed as the drive shaft. This result is accomplished by maintaining the sun gears 30, 42 and 5.3 locked for rotation in unison and in holding these sungears locked from rotation with respect to the driven shaft. This action results in holding the sun gears 30 and 42 from relative rotation, and as both of these gears are engaged by the double pinion unit 33, all of the gears are locked from relative rotation and the entire transmission rotates in unison.

When an over-drive speed of the driven shaft 15 is desired the sun gear 42 remains clutched to the driven shaft and simultaneously the sun gear .51 is held from rotation. The double pinion unit BI is then forced to rotate about the fixed sun gear 51, rotating the ring gear unit 44, 52 to rotatethe double pinion unit 33. As the sun gears 30 and 42 are clutched together against relative rotation the planet gear unit 33 can not rotate, therefore preventing relative rotation of,

the ring gear 44 with respect to the planet gear unit 33. Thus one epicyclic gear system is locked from rotation and as the sun gear of the other respect to the driven shaft l5, thus holding the corresponding epicyclic gear train locked from relative rotation and causing the driven shaft to remain locked to the ring gear unit 44, 52. However, in this speed ratio the sun gear 51 is released and the sun gear 53 is held from rotation, thus causing the double gear unit 6! to rotate gear unit 44, 52. Inthe transmission illustrated the speed ratio is 1 to 1.55 with respect to the drive shaft when thus controlled.

The clutch and brake system From the foregoing-description of the transmission operation, it will be obvious that various locking means are required for the sun gears 42, 53, and 57. .In order, to control rotation ofthese sun gears they are independently mounted on their respective sleeves l5, l1, and I9 and for convenience these respective sleeves are held from rotation or locked to rotate in unison as required.

The clutch holding the two planet'gear carriers lockedjor rotationin unison has already radially slidable in the s1ots'84.

at ases been described as clutch R. 1|A brake A is pro I vided for locking sleeve I9 stationary. A brake B is provided for locking sleeve I6 stationary.

A clutch C is provided for locking sleeve I8 to the driven shaft I5. A brake D is provided for lock- 5 ing sleeve lfistationary. AclutchEisprovided for holding sleeves I8 and I1 locked together. These mission illustrated may attain, together with the clutches and brakes which must be engaged to produce these ratios.

Speed Motor Driven B E D A R Reverse 5. 24 l 0 0 5.77 l '3.95 1 2.47 l 1.71 l. l l l 1.38 l 1.55

Attached to the end of the frustro-conicalhousing I0 opposite the end bearing the flange II, we provide a substantially cylindrical casing section I6. A similar section II adjoins the section 78 and a third section I9 adjoins the casing section 11. The section I is designed to enclose thebrake A. The section II is designed to accommodate a double acting clutch and brake, comprising brake D and clutch E. The casing section I9 is designed to accommodate a second double acting clutch and brake, comprisin brake B and clutch C respectively. An end plate 80 closes the sec tion I9 so as to form a complete housing.

The brake A is best illustrated in Figures 3 and 12. of the drawings. Th rotor hub BI is splined to the sleeve I9 to rotate therewith. -A ring-like web 82 extends outwardly from the hub BI to support a substantially circular rotor 93. The rotor 83 is slotted at angularly spaced points 8-9 to accommodate vanes 85 which are The casing section I8 is bored internally to fit closely adjacent the outer periphery of the rotor 83 throughout somewhat less than one-half the circumference thereof. A pair of opposed pockets 8? are provided, however, on'opposite sides of the rotor into which the vanes 85 may extend. The pockets 81 are provided with elongated cylindricalsegments 89 connected to the smaller diameter portions of the internal bore by inclined, cam portions 90, which guide the anes inwardly into the rotor or outwardly there rom. 1

The brake A is designed for the express purpose of holding the rotor 83,f rom rotation with respect to the casing section Hi. When hydraulic fluid is trapped in the pockets 81, and when the vanes project into these pockets, the rotor 83 is held from rotation. However, when the oil is allowed to escape from or to flow out of the pockets 87, or when the-vanes 85 are held retracted into the rotor, rotation of the rotor 83 with respect to-the casing section I6 is possible.

In order to hold the vanes 85 retracted to per- 5 in the vane.

mit free rotation of the rotor 83 within the casing section", we provide a plunger 9| having a point 92 thereon designed to engage in a recess 93 in each of the vanes 85. The plunger 9| is urged against its corresponding vane 85 by a spring 94 which is adjustably held in place by a plug 95. Thus as each vane 85 engages the inclined end '90 of a pocket B'L'and is retracted into the rotor 83, it will be engaged by the point 92 of the plunger 9i, unless means are provided for holding the plungers retracted. In other words, in the absence of any means for holding the plungers 9i retracted, each plunger will engage its corresponding vane as soon as the vane is retracted by rotation of the rotor with respect to the casing section I8, and will lock the vane in retracted position.

In order to hold the plungers 9| from engagement with the vanes we provide a hydraulic pressure passage 98 through the end wall 91 of the casing section 15, which communicates through a ring-shaped groove 98' with a transverse passage 99 through each vane 85 to the aperture 93 When pressure is exerted through the passages 98 and 99 in a manner which will be later described in detail, this pressurewill retract the plunger 92, thereby acting to withdraw the point 92 of the plunger from the aperture 93. The vanes are then free to move outwardly in theslots 84, being moved outwardly by centrifugal force and by springs I00 between the vanes and the rotor 83.

A hydraulic cushion to reduce shock of engagement is provided by the hollow interior of the rotor 83. This chamber within the rotor is always partially filled with air; and sleeved passages 98 communicate therewith in such a manner that fluid forwardly of the vanes 85 may be and I02. and permits relative rotation between the transmission housing I4 and the outer housing I0.

The end wall 9'7 of the casing section I6 supports a ball bearing I04 which separates the inner extremity of the wall 91 from the hub I05 of the rotor I08 of the combined clutch and brake mechanism E--D within the casin section 11. The hub, I05 is spline connected'at IllI to the sleeve I1 and the sun gear .53 mounted thereupon.

The manner in which the housing section II is constructed is best illustrated in Figures 2 and 3 of the drawings. A cam I09 is provided'with a hub H0, spline connected at HI to the sleeve I8 bearing the sun gear 42. This cam I09 is supported between the sides H2 and II 3 of the rotor I08 to be spline connected to the sleeve I1. The rotor I08 includes a series of slots IM for slidably supporting double acting vanes H5. The vanes I'I5 when moved inwardly may engage against the cam-surface IIG/of the inner cam member I 09, forming clutch E. On the other hand, when these vanes H5 are projecting out- -wardlyfrom the rotor I06 they may engage against the cam-shaped surface I II of the casing section 11, forming brake D. The purpose of the vanes H5 is to lock the rotor I05 with respect to the casing 11 when the vanes are projecting outwardly and to lock the rotor I05 and l1 the internal cam I09 for rotation in unison when these vanes are projecting inwardly.

Each vane I I5 is provided with a slot H9 in one surfacethereof leading toward the outer extremity of the vane. vided in the opposite side thereof. A plunger I2 I' is mounted adjacent each side of each vane H6 in the rotor I06 and positioned with its axis substantially normal to the plane surfaceof the adjacent vane II5. Each plunger I2I is provided with a tip end or point I22 designed to engage in the -slot H9 or I20 50 as to hold these vanes from inward or outward movement. Spring means I23 are provided for urging each plunger I2I into its cooperable slot H9 or I20. An adjustable plug I24 is provided for adjusting the tension of each spring I23.

Therefore, it should be noted that the plunger points I22 normally engage in a slot I20 to lock the vane self-contained within the outer periphery of the rotor I06, but permit the vanes to slide inwardly. However, upon retraction of the cooperable plungers the points I22 thereof are disengaged from the slots I20 to permit the vanes to slide outwardly. .The plungers I2I are retracted by oil under pressure passing through transverse passages II8 adjacent the vanes H5. The grooves II9 permit free outward movement of the vanes when outward pressure is exerted upon the same, and limit inwardmovement thereof.

The cooperable plungers I2I may be retracted by oil pressure passing through the cooperable passage I I8, allowing the vanes I I5 toslide inwardly.

When the vanes I I5 are in their outwardly projecting position-illustrated near the top of Figure 2 of the drawings, these vanesmay extend into the opposed pockets I25 formed in the casing section 11. Each pocket I25 includes an arcuated section I26 concentric with the rotor I06 and terminates in a cam incline I21 at each end thereof so as to guide the vanes II 5 inwardly or outwardly. Thus when the plungers I2I in the slots I20 are'retracted so that the vanes can move into ene gagement with the cam surface II1 ,of the casing section 11 the vanes gradually move outwardly along the cam incline I21 until they reachthe arcuated section I26 concentric with the driven shaft and remain on this'arcuated considerable period of time.

Hydraulic liquid in the pockets I25 may by-pass section for a the vanes II5 when the vanes are on the cam inclines I21 of the cam surface II1.- A pocket or recess I29 extending a portion of the width of the vanes II5 communicates with the cam'inclines I21 and with the control valve therefor, so that as soon as the vanes I I5 come in communi cationwith the cam inclines the pressure may equalize on opposite sides of the vanes. We, have so as to lock the rotor I06 with respect to'its casing I01. The vanes- I I5 are angularly spaced so that two opposed vanes are always in position A second slot I20 is-proportant as there is no great pressure on any one side of the vanes II5 during their sliding move-.

ment because the pressure is equalized on both sides of the vanes during their sliding movement.

The pocket or passage I29 is in the form of a passageway leading from each end of each pocket I25 to its respective control valve which will be later described. Intermediate the pockets or passages I29 we provide an arcuated closed segment 7 I30 between the cam portion I21 of the cam surfaces II1 of the casing section I1 which is longitudinally slotted except at its mid-point. When the outer ends of the vanes H5 are in engagement with the arcuated segment I30, these vanes are fully retracted into the rotor I05.

In order to cushion the action of the vanes H5 in holding the rotor-I06 from relative rotation with respect to the casing section 11 the rotor I06 is hollow and is divded into two axially spaced chamber separated by a central partition wall. Openings I3I through the outer wall of the rotor I06 lead to the interior thereof and the rotor may be partially filled with hydraulic fluid because of the fact that the openings I3I. into one of the chambers I32'are provided with inwardly extending sleeves I33. However, the entire chamber I32 can not fill with oil, but contains a certain amount .of air which may act as a cushion to the action of the vanes. In other words, when the vanes II5 are in the position shown in Figure 2, the hydraulic fluid trapped in the pockets I25, forwardly of the vanes II5 may be partially forced into the interior of the "rotor, compressing the air therein and decreasing shock by permitting the rotor to stop gradually.

For each vane H5 is provided a passage I28 through the casing connecting the slot I20 therethrough with the inner end of the vane. Hy-

. draulic fluid under pressure may pass through a hub IIO which is spline connected to the sleeve The cam surface I6 encircling the shaft I5. H6 is provided with opposed arcuate sections I34, but the arcuate portions I34 terminate at the points I35 where the surface blends into inclined cam portions I36. Each pair of opposed inclined cam portions I36 terminatedn a large diameter portion or cam point I31 of a diameter to fit closely 'within the inner surface I39 0! the rotor I06. In other words, the points I31 of the internal cam I09 closely contact the inner surface of the rotor I06,.while opposite halves of the cam surface IIB are formed by the arcuated portions I34. Thus it the vanes II5 are urged inwardly against the. cam surface II6, they will move to engagethe arcuated surface I26 of the opposed pockets I25. When one of the vanes II5 engages the cam incline I21 after traversing the entire length of the arcuate surfaces I26, the next adjacent vane is Just leaving the cam incline I21 at the other end of the pocket I25 and therefore is coming into operation; This is extrem y &9:

inwardly the greatest amount throughout contact with the arcuated portions] I34 of the surface. The vanes I I5-wlll then be urged outwardly by the inclined cam portions I36 until they are fully retracted into the rotor I06. The vanes' wilbthen travel down the next inclined cam portion I36 until they engage the next adjacent.

- '13 urged in one'direction by ,a spring I42. Passages I43 lead ,through the wall of the cam adjacent each inclined portionI36 thereof so that while. 1 the vanes H are in engagement with these inclined portions I36, hydraulic fluid may by-pass the blades. ber MI is in the position illustrated in Figure 3 of the drawings, the hydraulic fluid can freelyflow through the grooves I from one opening or passageway I 43 to the next. The wall of the cam I09 is solid adjacent the arcuated surfaces I34 and also at the opposite points I31 of the cam, the openings I43 being positioned between the extreme points of the cam and the arcuated surfaces I34 thereof.

When the vanes 'I I6 are inwardly projecting I Furthermore, while the valve mem--' relieve pressureon the vanes I65 when the vanes are engaging aportion'of the cam surface I66,

against the cam surface I I6 the hydraulic fluid and the cam I09 can not take place. Therefore when thus engaged these two elements must rotate in unison. v

In order to cushion the shock of engagement between the rotor I06 and the cam I09, we provide openings I through the inner wall of the rotor I06 leading into chambers I46, occupying onehalf of the hollow volume of the rotor and spaced axially from the'chamber I32 into which theopenings I 3| extend. These openings I45 are each provided with an outwardly extending/sleeve I41 which prevents the entire chamber from filling upwith hydraulic liquid and therefore provides an air cushion which may compress to some extent under pressure so as to cushion the shock of engagement between the elements I06 and I09.

The brake B and clutch C, illustrated in Figure 3, are virtually identical with the brake D and clutch E which have been described, with the exception of the hub structure. "The internal cam I49 of the clutch C .is identical to the internal cam I09 with the exception that the hub I thereof is of somewhat smaller diameter than the hub H0 and is spline connected at I5I directly to the driven shaft 15. A rotor I52, substantially identical to the rotor I05, is provided with a hub I53, spline connected at I54 to the sleeve I6. Externally of the hub I53 is pro- .vided a bearing 155 to separate the hub I53 from the end wall I56 of the casing section 11. This y casing end wall l56 extends between the side plate .I I2 of the rotor I06 and the-side plate I51 14 identical with the vanes H5 and the casing section 16 isflprovided with an -intemal cam surface I 66,- identical with the internal .cam surface .of the'casing section 11, illustrated'in Figure 2 of the drawings. Passages I61, identical with the pockets or passages I29,

which would tend to move the vanes longitudinally or permit such longitudinal movement.

In other words, a sectional view of the. brake B and clutch 0 contained within the casing section 19 wouldbe identical with the section shown in Figure -2, except for the fact that the cam I69 is keyed to the shaft I5,-rather than to the sleeve I6. The method of operation and construction of the brake B and clutch C is otherwise identical with that of brake D and clutch E.

The driven shaft I5 may operate any suitable device, but it most frequently is connected to a universal joint, such as I69. In such instance,

the end of the driven shaft I5 may be tapered, as.

at I10 for connection with a portion I1I of the universal point, and bearing means I12 may be:

provided between the hub I13 on the end of the closure plate and the casing section 19 ;for

this universal joint portion I1I.

' The control system I The clutch and brake construction in the halting of relative movement between the vari-' ous sleeves controlling the sun gears of our transmission have been described. border to con-, trol the transmission automatically, a control means is provided which will selectively engage the various clutch and brake elements and which will therefore permit successive relative speeds between the drive shaft and the driven shaft to be built up. This control means, for controlling.

the clutches and brakes which have been described, will now be described in detail. Similar control units are provided on opposite sides of the housing I0; but in the interests of simplicity,

but one control is illustrated in detail.

Gil

of any desired shape, but which, in the construcclosing the cam I49 between the rotor plates I51 and I59. The side plate I59 is supported by a.

bearing I60 encircling the driven shaft I5.

A ring-shaped slot I H 'is provided in' the cam I49 to accommodate the slidable valve I62 which is normally urged into open position by a spring I63. When urged in theopposite direction' to compress the spring I63, the valve I62'is in posi- The hub 23 of the transmission housing I4 is I provided with worm gear teeth Ilt-whih operate a gear I15 on a shaft iitextending transversely through the transmission housing "3., On each end ,of the shaft I16, we provide a pump I11 enclosed within an added casing portion I19 of the housing. I0. Asbest illustrated in Figure 5 of the drawings, the'pump I11 is provided with a'n'inlet passage I80, which extends into the interior of the transmission casing I0 to obtain oil from this casing interior. The pump I11 pumps the oil thus collected through an outlet passage I8I into ,a pressure chamber I82 which may be .tion illustrated, encircles a portion 'of the transmission casing I0 as best illustrated in Figure 4 j ofthe .drawings.

As the 'upper portion of the pressure chamber I82 is preferably filled with air, an oil pressure is thus built up in the chamber for the purpose which will be hereinafter more clearly set forth. Whensuflicient pressure is built up within the pressure chamber I82 the valve I 83 opens automatically to allow oilto-escape. The valve I83 is supported in an outlet-iport I64 and is urged by a spring I85 in position to close the .port I84. "Obviously the valve I83 will open under pressure to permit oil to flow into the chamber I 86. The amount of pressure which must be built up before the valve I83 will open may be regulated by the pressure adjustment nut I81, which adjusts in therotor m, J

.cl'usively through the aperture 2I9 through the aperture 2i I.

the tension of the spring I35. The valve I33 is inserted through a threaded port I89, normally closed by a cap I99 bearing the adjustment nut I91.

A butterfly valve I9I permits a metered amount of liquid to by-pass into the reservoir I92 formed within the transmission casing I9. Thus at idling speeds the pressure built up by the pumps IIl may be permitted to escape .past the valve I9I. An arm- I93 is connected to the shaft of the butterfly valve I9I so that the setting of this valve may be adjusted and a connection to this arm I99 may be made to any convenient location so as to control the engagement timing of the circling the hollow shaft I96 ofarotor I97. Openings I99 through the hollow shaft I96 provide constant communication between the interior passage 299 of the, shaft I96 and the passage I95 so that the volume flow chamber I86 may always .be in communication with the interior of the rotorv I91. The rotor I91 is constructed ,as best illustrated in Figures 4 and 9 of the drawings, the hollow passage 299 of the shaft I96 commu- I nicating with a radially extending passage 29I in the rotor, extending to the outer periphery thereof. The rotor I 91 includes a hollow cylindrical shell 292 having openings 293 and 294 therethrough on opposite sides of the passage 29L Thus it is obvious that oil from the volume flow chamber I86 may flow throughthe interior-shaft passage 299 and the passage 2 9 I and into the 'hollow cylindrical casing shell 295 forming a part of' the transmission housing I9, as best illustrated in Figure 4. 1 a

A sleeve 296 encircles the shell 292 and is provided with a radially extending partition wall 291 which is secured to the casing shell 295% 299 on opposite sides ot the partition wall 29L A projection -2I2 is provided on the lower end of the partition wall 291, which extends in the path of thesides of the passage 2M and which, there-. fore limits rotation of the rotor I9'I.' In other 7 words, the passage 29I may be positioned as shown, in communicatibn with the area on. both sides of the partition wall 291. However, by rotating the rotor I91 a few degrees in either direction, the passage -29 I may communicate solely. with the space to one side or the other of the partition wall 291', thus delivering oil either exor exclusively The shell :02 or the rotor m is connected to the shaft I96 by means of spaced spider arms 2".

. A disk m is positioned within the housing shell 295 tobe interposed between the rotor I91 and the'bo'dy of the crank case which forms a shoulider 2I5 against which the disk 21 rotates.- A

hub 2 on the disk 2 is internally bored with to by any suitable means, such as the pin 22I.

The shaft 220 is merely provided to synchronize the operation'ot the hubs 2I9 on both sides of the transmission.

The closure plate 22! secured in any suitable manner to the shell portion 295 of the housing acts to close the outer extremity of this casing. A manually operable handle 222 is provided with a suitable shaft 223vextending axially through the closure plate 22I. A planet gear carrier 22% is provided with a hub 225, pin connected to the shaft 223, and this planet gear carrier is equipped with axes 229 and planet gear .221. A sun gear 229 is secured to the closure plate 22I and is therefore held stationary with respect to the housing. The planet gears 221, illustrated in Figures 4 and -7 of the drawings, engage this sun gear 229 and also engage the internal ring gear 239, forming a part of a rotatable shell 23I of a diameter equal to that of the shell 293. A spiral spring 232, illustrated in Figures 4 and 6 of the drawings, is anchored at its inner end 239 to the planet gear carrier 229, while at its outer end 236, this spring 23." is connected to the rotor I97. This spring 232 farms a resilient connection between the rotatable shell 23I and the rotor I9! on the rotor I91 engages a cooperable projection 235 to positively rotate the two elements in unison when the handle 222 is operatedin the opposite direction. t

The disk 2 I4 is provided with a paddle or vane 239, best illustrated in Figure 9 of the drawings, which substantially fills the space between the shell 293, the shell- 23L and the outer housing 295. This vane 239 extends from the disk 2% to the closure plate 22 I so that when pressure is built up on one side of the vane due to the vol- I ume of oil within the housing 295, rotation of the disk 2 will be caused. The hub 219 of the dish 2 is provided with worm teeth 23? which are tion of the control valve 299 is caused by rotation-of the disk 2M, which in turn is rotated by oil pressure acting against the vane 236 mounted thereupon. A spring 238 returns the dish 2M to starting position when pressure against vane 236 is released. The exhaust passage from the controldevice is provided throughopenings 241 m the disk 2 I4, allowing'the fluid to flowthrough the outlet passage 242, about the'hub 2L6, and through the passage 243- around the shaft 229 leading into the oilreservoir within the casing, I9. It will the interior the rotor shell 292'and accordingly a from the int rior of the rotary sleeve 23I, which abuts against the rotor I91, and which has no exhaust. 5 An aperture 2 is provided in the shell 23I through which hydraulic fluid may flow. The position of this aperture tg-is regulated by rotation of the control handle 222 for the purpose which will be, hereinafter setiorth. The shell 95 23I is held in adjusted position by the ball detent 245 which is urged into one of a series of anguspring2l6.

Connected to the pressure passage I95 leading through-the transmission casing to the reservoir on the interior thereof, we provide a hydraulic fluid passage 241. A. butterfly valve 249 is mounted on a shaft 259 extending through the passage 2", and an arm 25I' ismounted on the shaft 259 externally of the housing for use in for movement in one direction. .A projection 239 designed to engage the gear 239 mounted on the end of the rotary control valve 299. Thus operatherefore be obvious that oil may escape from end wall to prevent the flow r fluid to the iariy spaced indentations in the sleeve 23I by a any suitable means to the accelerator of the en-- glue to which the transmission is mounted. As

' a result the butterfly valve 249 is closed at idling speeds of the motor and gradually opens to exhaust some of the oil being pumped by the pump IIl which is diverted back to the reservoir through the passage 241, and the amount of 011 thus by-passed increases as the speed of the engine'increases. This prevents the building up of an excessive volume of oil within the control casing. The pressure of the oil in chamber I86 is regulated by the foot accelerator, so that the more the accelerator is open, the slower will be rotation of the vane 2'36, and the slower will be the speed change in thetransmission. When valve 249 remains stationary,"the speed change increases while .the engine slows until a balance is reached.

Having now described the construction of the manually controlled means used for controlling the. engine, we will now explain the operation of this control. It will beunderstood that the purpose of the control is to regulate the position of the control valve 240, which controls the hydraulic fluid pressure to the various clutches and brakes. The-various passages from the control valve 24!) will be later described in detail.

When the drive shaft starts to rotate, the hub 23 starts to revolve and the worm gear-teeth I'M act to drive the gear I on the shaft H6. The

pump I1! is then set in motion pumping oil from within the casing I!) to the pressure chamber !82 which acts to build up pressure in'this pressure chamber. When th pressure reaches a predetermined maximum, the valve !83 opens, allow ing oil to flow into the passage !86. If the engine is rotated at an idling speed, sufficient oil will by-pass past the butterfly valve !9! to prevent high pressure from being built up within the control. Oil passing through the passage I86 is communicated through the opening 200 in the hollowshaft !'96 and through the passage This-oil m'ay flow back through the openings 2!!! and 2!! into the interior of the shell 202,'from whichposition it may escape through the openrotated by pressure against the vane 236 in a -counter -clockwise direction until the vane passes a portion of the opening 244, whereupon the fluid through the interior of the shells 202 and 235 in the manner which has been described. This rotation of the disk 2l4 acts through the gear teeth 23! and the gear 239 to rotate the valve 240 so as to apply the proper brakes and clutches to cause a reverse motion of the drive shaft i5.

Let us now say for example, that it is desired to rotate the shaft !5 in the lowest or first forward'speed. The control handle 222 is rotated in a clockwise direction until first forward speed is indicated. Clockwise rotation of the control handle 222 acts through the planet gear system described to rotate the shell 23! in a. clockwise direction. Tension is also exerted on the spring 232 to rotate the rotor I91 into its other extreme position. Accordingly the passage 2!!! is rotated out of communication with the opening 2!!) in the sleeve 203 and into communication with the opening 2!! in this sleeve. If the engine is travelling at idling speed, sufficient pressure will not bebuilt up to operate the control. Upon increasing the speed of the engine, however, pressure is built up which issues through the passage 2!]! and through the opening 2!! to exertpressure against the vane 233, tending to rotate this vane, and the disk 2M to which it is secured, in a clockwise direction, as viewed in Figure 9.

In first forward speed the opening 244 in the shell 23! is positioned in a clockwise direction from the vane 236. Thus in order to escape through this opening 244 to the exhaust the disk 2!4 .is rotated in a clockwise direction until the vane 236 passes a portion of the opening 244, al-

' lowing the hydraulic fluid to exhaust. Therefore, as long assufilcient speed is maintained in the lugs 24! in the disk 2! 4, then passing through passages 242 and 243 to the reservoir. Obviously in this neutral position or setting of the control illustrated in Figure 9 the control valve, 240 will not be operated.

Let us first'consider that the manual control I handle 222. is rotated in a counter-clockwise direction until the handle indicates reverse. In such an instance the projection 235 on the planet gear carrier 224 strikes the projection 234 on the rotor I91, rotating this rotor until the' passage 20! communicates solely with the openm mo in the shell 203. If the engine remains at idling speeds insuflicient pressure will be built up to actuate the control. However, during this rotation of the control handle 222 the shell 23! is rotated so that the opening 244 is in a slightly counter-clockwise direction from the vane 236. Therefore as the speed of the engine is increased,

hydraulic fluid under pressure will be forced driving unit the drive shaft will be rotated at first or lowest speed. For each successive forward at which the manual control handle is set deter-- mines the maximum speed ratio which may be attained for any setting of the control handle-the vane 236 rotating the disk '2l4. and the gear 23'! on the hub thereof, to rotate the gear 239 and the control valve 240. However, in order to at-.

tain this speed the transmission must by-pass through each 01 the lower speed ratios, as the vane 236 ,slowly revolves to its maximum position according to the" setting of the control handle 222. Accordingly, it it is desired to drive the driven shaft at the highest speed attainable, depending upon torque and engine speed, it is only necessary to move the'control handle to its extreme position to indicate seventh speed or super over-drive position. Then as the speed of the engine increases the vane 236 will successively pass through each of the first seven speeds until this 2!! or through theaperture 244 in the shell 23!.

As neither of these openings is uncovered in the starting. position of the vane 236, the disk 2 is vane finally reaches super over-drive position,-

whereupon additional hydraulic fluid pumped will by-pass through the exhaust opening 244. -'Accordingly when set at any maximum speed ratio' which is the greatest which can be attained for the engine speed andtorque relation.

As has been previously explained the fluid same.

- piston valve 216 is provided with into one extreme positionby the spring 26!. A

19 passes through the valve 163 and into the volume flow chamber I95. This chamber I95, as best illustrated in Figure 9. is connected by a passage 252 which leads to the-end of the control valve 246. The control valve 246 is hollow, having a passageway 253 passing lengthwise through the The control valve 246 is provided with four valve portions 254, 256, 256 and 251, which are of larger diameter than the intermediate connecting portions 259. 266, and 26L The larger diameter portions 254 through 251 fit closely within the valve cylinder 262 which forms a part of the casing l6.- Various passages are formed from the axial passage 253 to various. portions of the control mechanism in order to actuate these cooperating parts.

A cylinder 263 extends parallel to and adjacent the control valve cylinder 262. As best illustrated in Figures 1, 3, and 9 of the drawings, this control cylinder 263 is divided into three longitudinally spaced separate cylinders. The first of these cylinders 264 is separated from the pressure chamber I92 by means of an end wall 265 and is separated from the second aligned cylinder 266 by a partition wall 261. Similarly the cylinder 266 is separated from the next aligned cylinder 269 by the partition wall 216. The other end of the cylinder 269 is provided with an end wall A piston valve 212 is slidably positioned within the first cylinder 264 and is normally held in one extreme position by means of a spring 213. In preferred form the piston valve 212 is hollow so a to require a minimum amount of weight. A boss 214 on the end of the piston valve 212 engages the partition wall 261 in extreme position of the piston valve. thereby leaving a small space 216 between the end 01' the piston valve 212 and the wall 261.

The cylinder 266 is providedwith a piston valve 216 therein which is normally urged in one extreme position by a spring 211. A boss 219 on the spaces this valve from the wall 261 in extreme position thereof. The cylinder 269 a piston valve266 which is urged boss 262 on the piston valve 266 prevents this piston valve from engaging against the wall '216' in extreme position.

A passage 263 connects the left hand end of the cylinder 264 to the control'valve cylinder 262 V at a point opposite the enlarged portion 255 of 246. The right hand end of passage 285 extending with the valve cylinder 262 opposite the enlarged portion 255 of the control valve 246.- The space 261 encirclingthe'small diameter portion 2661s connected to theexhaust passage 265 by the passage 289. The left hand end of the cylinder 266 is connected by a passage 296 to the valve cylinder 262 opposite the enlarged diameter portion 256 of the control valve 246. Thus either end of the cylinder 264 may be subject to pressure depending upon the position of the control valve 246.

A passage 291 connects the right hand end of the cylinder 269 to the control valve cylinder 3,52

sses opposite the enlarged diameter portion 25601 the valve cylinder 262 opposite the enlarged diameter portion 251 of the valve 246. The space 293 encircling the small diameter portion 26! of the control valve 246 is connected to the exhaust presv sure passage 265 by a passage 294.

is connected by a passage 294 In Figures 2 and 3 of the drawings it will be. noted that a passage 295 extends through the shaft 15 axially thereof. This passage 295 communicates with the passage 15 leading to the valve chamber of the slidable valve 13. The other end of the passage 295 communicates through outwardly extending passage 296 to a collector groove 291 which communicates through the passage 299 with th cylinder 262 of the control valve 246 opposite the enlarged portion 251 thereof.

As best illustrated in Figure 13 of the drawings, the control valve 246 is provided with a series of angularly spaced radially extending openings, that are in communication with the passage 253 through the control valve. In other angular positions of the control valve, slots communicate with the spaces 261, 293, and 366 encircling the small diameter portions 266, 26l, and 259 respectively of the valve 246. Thus at all times when the passages 264, 263, 266, 296, 29l, 292, and 299 are not in communication with the radially extending openings through the valve, they are in communication with one of the spaces such as261, 293, or 366. These spaces respectively are connected'to the 'exhaust passage 285 through exhaust passage 269, 294, and 36!.

The end 362 of the control valve 246 is also of reduced diameter and the space 363 encircling the same communicates with the exhaust pressure passage 285 through a'passage 364. Thus all of the spaces encircling the small diameter portions of the valve 246 are connected to the exhaust. The arrangement of the pressure openings and exhaust openings in the valve 246 is best illustrated in Figure 13 of the drawings. It will be noted that five pressure passages 365 are provided in the large diameter portion 251 of the valve 246 which, in various rotative positions of this valve, communicates with the passage 292 so as to permit pressure to enter the passage 299 which controls the position of the valve 13. It will also be noted that four slots 366 are'provided in this large diameter portion 251 communicating I larly spaced radially extending passages 361 are provided which may communicate with the passage 292 at the left handend of the cylinder 269.

Likewise six slots 369 are provided in the, large diameter portion .251 which communicates with the space 293 encircling the small diameter portion 26f of the valve 246. As a result in three rotative positions of the valve 361, pressure will be communicated to the left hand end of the cylinder 269, while in all other rotatative positions of the valve the passage 292 will be in communication with the exhaust. I I

' The large portion 256 of the valve 246 is provided with two angularly spaced radially extending passages 3l6 which register with the passage 292 in two different rotative positions of the valve 246. In seven other rotative positions of the valve, slots 3 are provided which communicate with the space 293 encircling the small diameter portion 26I of the valve. Therefore, when the valve 249 is in 'two diiferent rotative positions, pressure will be communicated to the left hand end of the cylinder 269, whereas in all other rotative positions thereof, the passage 292 is communicated with the exhaust..

The large diameter portion 256 of the valve 249 is likewise provided with three spaced radially extendingpassages 3I2 communicating with the,

pressure passage 253 extending axially of the valve so that inthree rotative positions of the valve, these passages 3I2 may communicate with the passage 299 at the left hand end of the cyl-v inder 268. Six slots SIS are likewise provided in the enlarged portion 256 so that when the valve is at any other rotative position the passage 290 will communicat with the exhaust through the space 281i.

The enlarged portion 255 of the valve 259 is- 293 leading to th left hand end of the cylinder 263 in three difierent rotative positions of the valve 249. In all other positions of the valve the passage 283 is connected to the space 390,

- and therefore to the exhaust passage through angularly spaced slots 3I'I in the large diameter portion 255.

a In summing up the description of the control valve 249- it will be obvious that the passage 299 is either in communication with pressure or with exhaust through the passage 394. The passage,

with pressure or other exhaust by way of the passage 299. Similarly the passage 29! is either subjected to pressure or to' exhaust through the passage 294. The passage 299 is either subjected f to pressure or to exhaust through the passage :99. The passage 296 is either subjected to pressure, or else is subjected to exhaust through the passage 299. The passage 293 similarly is either sub-- .iected to pressure or to exhaust through the pas-J- sage 9M.

292 is likewise always either in communication 22 passage 3| 9 and by the passage 320 to the 'right end of the groove I49 in which the valve II is located. This pressure is transmitted through the-radially extending opening 32I, leading to -the'area between the cam I99 and the inner surface I39 of the rotor I08, for the purpose of creating a pressure on the inner ends of the vanes II5 and at the same time the pressure from the passage 3I9 enters the passage M8 to retract the plungers I2I, allowing outward movement of the vanes H5 in the rotor I96. As the oil is thus forced to travel through the passageway I29, it is intercepted by the piston 21$. :This will retard rotation of the rotor' I96 as the oil pressure is built up against the outward ends of. the vanes 5, thus locking the brake D.

When a neutral speed is desired the control valve 240 may be rotated so that all of the various passages are communicated with the exhaust, and none of the clutches and brakes are engaged with the exception of the normally engaged reversing clutch R. No novernent is transmitted from the' drive shaft to. the driven shaft when the control valve is in. this position.

-When a first forward speed-is desired, the control valve 240 is turned so that pressure. is directed through the opening 3! 6 to the passage 283, leading to the left hand end of the cylinder 266.1 This action tends to force the piston 272 to the right, thereby closing the. passages 322 noted in Figures 3 and 12. Before the piston 212 has closed the passages 322, the vanes are released by the points 92 in the aperture 93 of the said vanes. Oil pressure passes through the passageway 96; groove 98, and passage 99 against the plunger 9!, compressing the spring 96. The springs 84 will then force the vanes outwardly into the space or pockets '81. Thus the oil flow created by the vanes will be intercepted'by the piston 212 which in turn will bring the rotor '83 to a standstill. Ac-

cordingly in the manner which has been described /thevanes 85 willbe stopped from rotation with respect to the casing section I6.

In order to provide a second forward speed, the

brake-A-is released and the brake B is engaged.

The clutch'R; which is normally engaged remains" engaged in thisspeed. The brake B is engaged by pil'pressure passing through openings 3m in When a reverse speed is desired, it is necessary 1 that the valve I3 remain closed so that the clutch R. remains engaged and so that the brake D be engaged. Accordingly. in reverse position pressure-from the interior of the control. valve is com-- municated only through thepass'age 3" to the passage 286. Pressure in the passage 286 creates pressure on the right hand sideof the piston 216 which forces this piston tothe left,-as viewed .in Figures 1 and 3. Accordingly the piston valve .216 closes. the passages I29 of the brake unit D. At the same time the vanes 5 will be forced outwardly by thefldidpressure passing through the passage-M9 and the passage 32d and into the opening I53 for creating pressure upon the innerend of the vanes 5. At the same time the pressure leaving from the passageway M9" plungers I2 i 'to disengage through IIB forces the the vaneIIB. This will create a pressurebe tween the pistons 216 and the vane's H5 and retard the rotor I06 to a standstill( the valve 249, which leads to the passage 2M at the right end of the cylinder 269. Pressure at the right hand end of the cylinder 269 acts through the passages2329 and 324 to enter the groove I6I in which the valvel62 is located. 'This pressure passes through the opening I64 to the space between the cam I49 and the rotor I-52 to urge the vanes 'I65, outwardly. Pressure also acts through the passages II8 adjacent the vanes I65 to retract the corresponding plungers I 2| and to release'the vanes I65 for movement outwardly into engagement with the cam surface I66 of the easing section I9. simultaneously the piston 299 is forced to the left. closing the passage I61 and therefore stopping rotation of the vanes I65 with respect to the casing section 19. As a result the sun. gear 42 is held from rotation, providing a second forward speed as'has been previously de- A scribed.

As noted in Figure 3 of the drawingsl the right hand end of the cylinder 266 is connected by a.

In the remaining five speeds the clutch R is continuously disengaged. This is accomplished by communicating oil from the passage 353 in the valve 240, through the valve port 305, the passages 299, 291. 296', and 2.95 tothe passage I5 communicating with the valvechamber 'I2-of the valve I3. This pressure forces'the 'valve 13 to the left, opening a passage II, whereupon the oil 

